KR102318123B1 - Scroll compressor - Google Patents

Abstract

A scroll compressor according to the present invention comprises: a first wrap; and a second wrap engaged with the first wrap and eccentrically coupled with respect to the center of rotation of the rotation shaft to form a compression chamber moving toward the center together with the first wrap while rotating with respect to the first wrap; Including, wherein the height of at least one of the first lap and the second lap is formed to have at least two or more inclined processing amounts that decrease toward the center, the amount of inclined processing is determined by the amount of inclined processing on the center side. By forming a larger than the edge-side bevel processing amount, friction loss and abrasion of the lap can be suppressed and damage of the lap can be prevented.

Description

Scroll Compressor {SCROLL COMPRESSOR}

The present invention relates to a scroll compressor, and more particularly, to a compressor in which a compression unit is located below a transmission unit.

A scroll compressor is a compressor that engages with a plurality of scrolls and performs a relative rotational motion while forming a compression chamber composed of a suction chamber, an intermediate pressure chamber, and a discharge chamber between both scrolls. Such a scroll compressor can obtain a relatively high compression ratio compared to other types of compressors, and a stable torque can be obtained by smoothly performing refrigerant suction, compression, and discharge strokes. Accordingly, scroll compressors are widely used for refrigerant compression in air conditioners and the like. Recently, a high-efficiency scroll compressor with an operating speed of 180 Hz or higher by reducing the eccentric load has been introduced.

The scroll compressor may be divided into a low-pressure type in which a suction pipe communicates with an inner space of a casing forming a low-pressure part, and a high-pressure type in which a suction pipe communicates directly with a compression chamber. Accordingly, the low-pressure type driving part is installed in the suction space of the low-pressure part, whereas the high-pressure type driving part is installed in the discharge space of the high-pressure part.

Such a scroll compressor can be divided into an upper compression type and a lower compression type depending on the positions of the driving unit and the compression unit. When the compression unit is located above the driving unit, it is called an upper compression type. On the contrary, when the compression unit is located below the driving unit, it is called a bottom compression type.

In a scroll compressor, as the pressure in the compression chamber increases, the orbiting scroll receives a gas force in a direction away from the fixed scroll. Then, as the orbiting scroll moves away from the fixed scroll, leakage between the compression chambers occurs and the compression loss increases.

In consideration of this, in the scroll compressor, a tip seal method of inserting a sealing member into the front end surfaces of the fixed wrap and the orbiting wrap is applied, or a back pressure chamber forming an intermediate pressure or a discharge pressure is formed on the rear surface of the orbiting scroll or the fixed scroll to form the back pressure chamber. The back pressure method is applied in which the orbiting scroll or the fixed scroll is pressurized by the opposing scroll with the pressure of

In particular, in the back pressure method, a method is known in which a sealing member is installed between the rear surface of the orbiting scroll (or the rear surface of the fixed scroll) and a frame corresponding thereto so that a back pressure chamber is formed inside or outside the sealing member. In the back pressure method using such a sealing member, an annular groove is formed in one member constituting the thrust surface, and an annular sealing member having a square cross-section is inserted into the annular groove. Then, the medium pressure refrigerant compressed in the compression chamber during operation of the compressor flows into the annular groove, and the sealing member is lifted up by the intermediate pressure pressure and is in close contact with the opposing member, thereby forming a back pressure chamber.

However, in the conventional scroll compressor as described above, the back pressure applied to the central portion of the orbiting scroll is greater than the back pressure received by the edge portion, so that the central portion of the orbiting scroll is excessively pressed in the direction of the fixed scroll. Then, a portion of the fixed lap adjacent to the discharge end may excessively adhere to the orbiting scroll, or a portion adjacent to the discharge end of the orbiting lap may excessively adhere to the fixed scroll. At the same time, the central portion of the fixed wrap or orbiting wrap is deformed while being bent outward by receiving gas force and centrifugal force in the direction of the edge, friction loss or wear occurs between the fixed wrap or the orbiting wrap and the scroll facing it, resulting in compressor efficiency this may be lowered.

Also, in the conventional scroll compressor as described above, in the case of a so-called through-axis scroll compressor in which the rotary shaft overlaps the compression chamber in the radial direction, the rotary shaft penetrates and engages the central portion of the fixed scroll, so that the discharge end of the fixed wrap is connected to the rotary shaft. This could not extend to the center of the fixed scroll sufficiently, and thus the rigidity of the discharge end of the fixed lap was weakened, so that the fixed lap was severely bent or the discharge end of the fixed lap was broken. Furthermore, as disclosed in Korean Patent Registration No. 10-1059880, when the compression ratio of the compression chamber is increased by changing the fixed wrap and the orbiting wrap to an atypical shape, the discharge end of the fixed wrap is more severely deformed and damaged. In this case, even when the lap support force is increased by forming a protrusion at the discharge end of the fixed lap, the lap deformation due to the increase in the compression ratio cannot be completely suppressed, and the reliability of the compressor may be lowered due to friction loss or wear or rupture of the lap.

Korean Patent No. 10-1059880

It is an object of the present invention to provide a scroll compressor capable of preventing friction loss or wear while optimizing the height of the discharging end of the lap while the discharging end of the lap excessively closely adheres to the face plate portion of the scroll.

Another object of the present invention is to provide a scroll compressor capable of suppressing breakage while excessively deforming the vicinity of the discharge end of the lap by optimizing the height of the discharge end of the lap.

Another object of the present invention is to optimize the height of the discharge end of the fixed wrap even when the rotating shaft passes through the fixed scroll and overlaps the compression chamber in the radial direction to prevent excessive deformation or breakage of the discharge end of the fixed wrap It is intended to provide a scroll compressor capable of increasing the efficiency and reliability of the compressor through this.

In order to achieve the object of the present invention, there may be provided a scroll compressor characterized in that the front end surface of the wrap formed on one of the two members sliding with each other is formed to have at least two inclination angles.

Here, the inclination angle may be formed such that a portion adjacent to the discharge side has the largest inclination angle.

In addition, in order to achieve the object of the present invention, the first wrap; and a second wrap engaged with the first wrap and eccentrically coupled with respect to the center of rotation of the rotation shaft to form a compression chamber moving toward the center together with the first wrap while rotating with respect to the first wrap; Including, wherein the height of at least one of the first lap and the second lap is formed to have at least two or more inclined processing amounts that decrease toward the center, the amount of inclined processing is determined by the amount of inclined processing on the center side. A scroll compressor may be provided, characterized in that it is formed to be larger than the edge-side inclined processing amount.

Here, when the center side of the first wrap or the second wrap is referred to as a discharge end based on the rotation angle of the rotation shaft, and the discharge end is 0°, the portion formed by the center side inclined processing amount is the It may be formed to include at least a portion of the range of 0 to 60° based on the rotation angle of the rotation shaft.

In addition, a rotation shaft coupling portion is formed in the center of the second wrap so that the rotation shaft overlaps and is coupled to the second wrap in a radial direction, and a concave portion for reducing the thickness of the wrap is formed on an outer surface of the rotation shaft coupling portion, and the first A protrusion may be formed at the discharge end of the lap to engage the concave portion, and the portion formed by the amount of inclined processing toward the center may include the protrusion.

In addition, in order to achieve the object of the present invention, a first end plate portion in which a bearing hole through which the rotation shaft passes is formed in the center and a discharge port is formed around the bearing hole, and a first protruding portion formed on one side of the first end plate portion a first scroll comprising a wrap; and a second end plate in which a rotating shaft coupling portion is formed so that a rotating shaft passing through the bearing hole of the first scroll is eccentrically coupled to the central portion, and is formed to protrude from one side of the second end plate and engage with the first lap to form a compression chamber together. a second scroll including a second lap forming a second lap; including, at least one of a front end surface of the first wrap facing the second end plate portion and a front end surface of the second wrap facing the first end plate portion The front end surface is formed to have a plurality of inclined surfaces so that the height of the lap is lowered toward the center, and among the plurality of inclined surfaces, the second inclined surface adjacent to the outlet has a larger inclination angle than the far first inclined surface, characterized in that A scroll compressor may be provided.

In addition, the second inclined surface may be formed over the entire second inclined surface along a traveling direction of the first lap or the second lap.

In addition, the second inclined surface may be formed on a portion of the second inclined surface along a traveling direction of the first lap or the second lap.

In addition, the second inclined surface may be formed at an edge of the side on which the gas force acts among both edges constituting the front end surface of the first wrap or the second wrap.

In addition, the second inclined surface may be formed with at least one inclination angle.

In addition, a plurality of inclination angles of the second inclined surface may be formed, and the plurality of inclination angles may be formed to be larger as they are adjacent to the discharge end of the first lap or the second lap.

In addition, a concave portion for reducing the thickness of the wrap is formed on the outer surface of the rotation shaft coupling portion, a protrusion is formed at the discharge end of the first lap to engage the concave portion, and the second inclined surface may include the protrusion have.

In addition, in order to achieve the object of the present invention, a casing in which oil is stored in the inner space; a driving motor provided in the inner space of the casing; a rotating shaft coupled to the driving motor; a frame provided under the driving motor; a first scroll provided under the frame, having a first wrap formed on one side thereof, a bearing hole through which the rotation shaft passes, and a discharge port formed around the bearing hole; and a second wrap engaged with the first wrap is formed, the rotation axis is eccentrically coupled to overlap the second wrap in a radial direction, and a pivoting motion with respect to the first scroll is formed between the first scroll and the first scroll. a second scroll forming a compression chamber; It is provided between the frame and the second scroll to separate the interval between the frame and the second scroll into an inner space on the center side and an outer space on the edge side, and the oil sucked through the rotation shaft flows into the inner gap and back pressure and a sealing member for forming a seal, wherein at least one of a front end surface of the first wrap protruding downward toward the second scroll and a front end surface of the second wrap protruding upward toward the first scroll is formed. The front end surface is formed to have a plurality of inclined surfaces so that the height of the lap is lowered toward the center, and among the plurality of inclined surfaces, the second inclined surface adjacent to the outlet has a larger inclination angle than the far first inclined surface, characterized in that A scroll compressor may be provided.

Here, when the discharge end of the first lap or the second lap is 0° based on the rotation angle of the rotation shaft, the portion formed by the center-side inclined processing amount is 0 to the rotation angle of the rotation shaft. It may be formed to include at least a portion of the 60° range.

And, when the maximum height of the first lap or the second lap is H1, the amount of inclined processing on the first inclined surface is H2, and the amount of inclined processing on the second inclined surface is H3, H2 < [(0.001 ~ 0.002) × H1]mm, H3 > [(0.01~0.03) × H1]mm can be satisfied.

In addition, a rotation shaft coupling portion is formed in the center of the second wrap so that the rotation shaft overlaps and is coupled to the second wrap in a radial direction, and a concave portion for reducing the thickness of the wrap is formed on an outer surface of the rotation shaft coupling portion, and the first A protrusion may be formed at the discharge end of the wrap to engage the concave portion, and the second inclined surface may include the protrusion.

The scroll compressor according to the present invention is formed by optimizing the lap height of the portion adjacent to the discharge end of the fixed wrap or the orbiting wrap, thereby minimizing the lap deformation of the discharge end at the center side that is subjected to relatively high back pressure and gas force. It is possible to prevent excessive contact with the opposing scrolls, thereby reducing friction loss or abrasion between the scrolls, thereby increasing compressor efficiency.

In addition, by optimizing the lap height of the portion adjacent to the discharge end of the fixed lap or the orbiting lap, it is possible to suppress deformation of the discharging end of the central portion of the fixed lap or the orbiting lap by bending radially outward, through which the compression It is possible to increase the compressor efficiency by suppressing seal leakage, and at the same time suppress the breakage of the wrap to increase the reliability of the compressor.

In addition, even when the discharging end of the fixed lap is located far from the center of the fixed scroll because the rotating shaft passes through the center of the fixed scroll, the lap height at the portion adjacent to the discharging end is optimized by optimizing the friction or abrasion between the fixed lap and the scroll. It is possible to increase the efficiency and reliability of the compressor by preventing deformation or breakage of the fixed wrap.

1 is a longitudinal cross-sectional view showing a lower compression type scroll compressor according to the present invention;
2 is a cross-sectional view showing the compression part in FIG. 1;
Figure 3 is a front view showing a part of the rotation shaft to explain the sliding part in Figure 1,
4 is a longitudinal sectional view showing the oil supply passage between the back pressure chamber and the compression chamber in FIG. 1;
5 is a schematic diagram showing the amount of deformation in the vicinity of the discharge end of the first lap in the scroll compressor according to FIG. 1 analyzed for each part;
6 is a schematic view showing the shape of the wrap in the portion with the largest amount of deformation in FIG. 5 from the front;
7 is a plan view showing a first scroll according to the present embodiment;
Fig. 8 is a schematic view showing the unfolding of the first wrap in Fig. 7;
9A is a schematic view for explaining an embodiment of the second inclined surface according to the present embodiment in FIG. 7, and FIG. 9B is a sectional view "IV-IV" of FIG. 9A;
10A is a schematic diagram showing another embodiment of the second inclined surface according to the present embodiment in FIG. 7, and FIG. 10B is a sectional view "V-V" of FIG. 10A;
11 is a graph comparing and analyzing compressor efficiency and reliability according to each inclined processing amount when the first scroll according to FIG. 7 is applied;
12 to 13B are schematic views showing other embodiments of the second inclined surface according to the present embodiment developed.

Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings. However, hereinafter, for convenience, in a lower compression type scroll compressor in which the compression part is located below the transmission part, a scroll compressor of a type in which the rotation shaft overlaps on the same plane as the orbiting wrap will be described as a representative example. This type of scroll compressor is known to be suitable for application to a refrigeration cycle under high-temperature and high-compression ratio conditions.

1 is a longitudinal cross-sectional view showing a lower compression type scroll compressor according to the present invention, FIG. 2 is a cross-sectional view showing the compression part in FIG. 1, and FIG. 3 is a front view showing a part of the rotating shaft to explain the sliding part in FIG. FIG. 4 is a longitudinal cross-sectional view illustrating the oil supply passage between the back pressure chamber and the compression chamber in FIG. 1 .

Referring to FIG. 1 , in the lower compression scroll compressor according to the present embodiment, an electric part 20 that forms a driving motor and generates a rotational force is installed inside the casing 10 , and the lower side of the electric part 20 is A compression unit 30 for compressing the refrigerant by receiving the rotational force of the electric part 20 with a predetermined space (hereinafter, referred to as an intermediate space) 10a may be installed.

The casing 10 includes a cylindrical shell 11 constituting an airtight container, an upper shell 12 that covers the upper portion of the cylindrical shell 11 to form an airtight container, and a lower portion of the cylindrical shell 11 to form an airtight container together. At the same time, it may be formed of a lower shell 13 forming a storage space 10c.

The refrigerant suction pipe 15 penetrates through the side of the cylindrical shell 11 to directly communicate with the suction chamber of the compression unit 30, and the upper portion of the upper shell 12 communicates with the upper space 10b of the casing 10 A refrigerant discharge pipe 16 may be installed. The refrigerant discharge pipe 16 corresponds to a passage through which the compressed refrigerant discharged from the compression unit 30 to the upper space 10b of the casing 10 is discharged to the outside, and the upper space 10b is a kind of oil separation space. The refrigerant discharge pipe 16 may be inserted to the middle of the upper space 10b of the casing 10 so as to be formed. And in some cases, an oil separator (not shown) that separates oil mixed with the refrigerant is installed in the inside of the casing 10 including the upper space 10b or in the upper space 10b by connecting to the refrigerant suction pipe 16. can be

The electric part 20 includes a stator 21 and a rotor 22 rotating inside the stator 21 . The stator 21 has teeth and slots forming a plurality of coil winding parts (unsigned) along the circumferential direction on its inner circumferential surface, so that the coil 25 is wound, and between the inner circumferential surface of the stator and the outer circumferential surface of the rotor 22 . _{A second refrigerant passage P G2} is formed by combining the gap and the coil winding portion. Accordingly, the refrigerant discharged to the intermediate space 10c between the transmission unit 20 and the compression unit 30 through the first refrigerant passage P _{G1 to be described later is a second refrigerant passage formed in the transmission unit 20 (} P _G2 ) is moved to the upper space (10b) formed on the upper side of the transmission unit (20).

And a plurality of decut (D-cut) surfaces 21a are formed on the outer peripheral surface of the stator 21 in the circumferential direction, and the decut surfaces 21a are formed so that oil passes between the inner peripheral surface of the cylindrical shell 11 and the inner peripheral surface of the cylindrical shell 11. One oil passage P _O1 may be formed. Accordingly, the oil separated from the refrigerant in the upper space 10b moves to the lower space 10c through _{the first oil passage P O1} and the second oil passage P _{O2 to be described later.}

On the lower side of the stator 21 , a frame 31 constituting the compression part 30 at a predetermined interval may be fixedly coupled to the inner circumferential surface of the casing 10 . The frame 31 may be fixedly coupled to the outer circumferential surface by shrink-fitting or welding the outer circumferential surface to the inner circumferential surface of the cylindrical shell 11 .

And an annular frame side wall part (first side wall part) 311 is formed at the edge of the frame 31, and a plurality of communication grooves 311b are formed on the outer peripheral surface of the first side wall part 311 along the circumferential direction. can be The communication groove 311b forms _{a second oil passage P O2} together with the communication groove 322b of the first scroll 32 to be described later.

In addition, a first bearing portion 312 for supporting the main bearing portion 51 of the rotation shaft 50 to be described later is formed in the center of the frame 31 , and the main bearing portion of the rotation shaft 50 is formed in the first bearing portion. The first bearing hole 312a may be formed through in the axial direction so that the 51 is rotatably inserted and supported in the radial direction.

In addition, a fixed scroll (hereinafter, referred to as a first scroll) 32 may be installed on a lower surface of the frame 31 with an orbiting scroll (hereinafter, referred to as a second scroll) 33 eccentrically coupled to the rotating shaft 50 therebetween. The first scroll 32 may be fixedly coupled to the frame 31 , or may be coupled to be movable in the axial direction.

Meanwhile, in the first scroll 32 , a fixed end plate portion (hereinafter, referred to as a first end plate portion) 321 is formed in a substantially disk shape, and the edge of the first end plate portion 321 is coupled to the lower surface edge of the frame 31 . A scroll sidewall portion (hereinafter, referred to as a second sidewall portion) 322 may be formed.

A suction port 324 through which the refrigerant suction pipe 15 and the suction chamber communicate is formed through one side of the second side wall portion 322, and the central portion of the first end plate portion 321 communicates with the discharge chamber to discharge the compressed refrigerant. Discharge holes 325a and 325b may be formed. Only one discharge port 325a and 325b may be formed to communicate with both the first and second compression chambers V1 and V2, which will be described later, but are independent of each of the compression chambers V1 and V2. A plurality may be formed to communicate with the .

And the communication groove 322b described above is formed on the outer circumferential surface of the second side wall part 322, and the communication groove 322b is the communication groove 311b of the first side wall part 311 and the oil recovered together with the lower space. _{A second oil passage P O2} for guiding to (10c) is formed.

Also, a discharge cover 34 for guiding the refrigerant discharged from the compression chamber V to a refrigerant passage to be described later may be coupled to the lower side of the first scroll 32 . The discharge cover 34 has an inner space that accommodates the discharge ports 325a and 325b, and at the same time receives the refrigerant discharged from the compression chamber V through the discharge ports 325a and 325b in the upper space of the casing 10 ( 10b), more precisely, it may be formed to accommodate the inlet of _{the first refrigerant passage P G1} guiding into the space between the transmission unit 20 and the compression unit 30 .

Here, the first refrigerant flow path ( _PG1 ) is the inside of the flow path separation unit 40, that is, the second side wall portion 322 of the fixed scroll 32 on the inner side of the flow path separation unit 40 from the side of the rotation shaft 50 side. and the first sidewall portion 311 of the frame 31 may be sequentially formed. Accordingly, on the outside of the flow path separation unit 40 , the above-described second oil flow path P _O2 is formed to communicate with the first oil flow _{path P O1 .}

And on the upper surface of the first end plate portion 321, a fixed wrap (hereinafter, referred to as a first wrap) 323 may be formed in engagement with a turning wrap (hereinafter, referred to as a second wrap) 33 to be described later to form a compression chamber V. have. The first wrap 323 will be described later along with the second wrap 332 .

In addition, a second bearing part 326 for supporting a sub-bearing part 52 of the rotation shaft 50 to be described later is formed in the center of the first head plate part 321 , and the second bearing part 326 is provided in the axial direction. A second bearing hole 326a may be formed therethrough to support the sub-bearing part 52 in a radial direction.

Meanwhile, in the second scroll 33 , the orbiting end plate portion (hereinafter, referred to as the second end plate portion) 331 may be formed in a substantially disk shape. A second wrap 332 may be formed on a lower surface of the second end plate 331 to be engaged with the first wrap 322 to form a compression chamber.

The second wrap 332 may be formed in an involute shape together with the first wrap 323, but may be formed in various shapes in which a plurality of other curves are connected. For example, as shown in FIG. 2 , the second wrap 332 has a shape in which a plurality of arcs having different diameters and origins are connected, and the outermost curve may be formed in an approximately elliptical shape having a major axis and a minor axis. . The first wrap 323 may likewise be formed.

In the central portion of the second end plate 331, the inner end of the second wrap 332 is formed, and an eccentric portion 53 of the rotation shaft 50, which will be described later, is rotatably inserted and coupled to the rotation shaft coupling portion 333. direction may be formed through.

The outer periphery of the rotation shaft coupling part 333 is connected to the second wrap 332 to form a compression chamber V together with the first wrap 322 in the compression process.

In addition, the rotation shaft coupling portion 333 is formed to have a height overlapping with the second wrap 332 on the same plane, so that the eccentric portion 53 of the rotation shaft 50 overlaps with the second wrap 332 on the same plane. can be placed in Through this, the repulsive force and the compressive force of the refrigerant are applied to the same plane with respect to the second end plate and cancel each other out, so that the inclination of the second scroll 33 due to the action of the compressive force and the repulsive force can be prevented.

In addition, the rotation shaft coupling portion 333 has a concave portion 335 engaged with the protrusion 328 of the first wrap 323 to be described later is formed on an outer peripheral portion opposite to the inner end of the first wrap 323 . One side of the concave portion 335 is formed with an increasing portion 335a increasing in thickness from the inner periphery to the outer periphery of the rotary shaft coupling portion 333 on the upstream side along the formation direction of the compression chamber V. This lengthens the compression path of the first compression chamber V1 just before discharge, and consequently makes it possible to increase the compression ratio of the first compression chamber V1 close to the pressure ratio of the second compression chamber V2. The first compression chamber V1 is a compression chamber formed between the inner surface of the first wrap 323 and the outer surface of the second wrap 332 , and will be described later separately from the second compression chamber V2 .

The other side of the concave portion 335 is formed with an arc compression surface (335b) having an arc shape. The diameter of the arc compression surface 335b is determined by the inner end thickness (ie, the thickness of the discharge end) of the first wrap 323 and the turning radius of the second wrap 332 , the inner side of the first wrap 323 . When the end thickness is increased, the diameter of the arc compression surface 335b is increased. Due to this, the thickness of the second wrap around the arc compression surface 335b may also be increased to ensure durability, and the compression path may be lengthened so that the compression ratio of the second compression chamber V2 may be increased accordingly.

In addition, in the vicinity of the inner end (suction end or start end) of the first wrap 323 corresponding to the rotation shaft coupling portion 333, a projection 328 protruding toward the outer periphery of the rotation shaft coupling portion 333 is formed, the projection ( A contact portion 328a that protrudes from the protrusion and engages with the concave portion 335 may be formed in the 328 . That is, the inner end of the first wrap 323 may be formed to have a greater thickness than other portions. Due to this, the lap strength of the inner end that receives the greatest compressive force among the first laps 323 may be improved, and thus durability may be improved.

Meanwhile, the compression chamber V is formed between the first end plate portion 321 and the first wrap 323 , and between the second wrap 332 and the second end plate portion 331 , and is sucked along the moving direction of the wrap. The chamber, the intermediate pressure chamber, and the discharge chamber may be continuously formed.

As shown in FIG. 2 , the compression chamber V includes a first compression chamber V1 formed between the inner surface of the first wrap 323 and the outer surface of the second wrap 332 , and the first wrap 323 . The second compression chamber V2 formed between the outer surface and the inner surface of the second wrap 332 may be formed.

That is, the first compression chamber (V1) includes a compression chamber formed between the two contact points (P11, P12) formed by contacting the inner surface of the first wrap 323 and the outer surface of the second wrap 332, and , the second compression chamber (V2) includes a compression chamber formed between the two contact points (P21, P22) generated by the contact between the outer surface of the first wrap 323 and the inner surface of the second wrap (332).

Here, the first compression chamber (V1) just before the discharge is the center of the eccentric, that is, the center of the rotation shaft coupling portion (O) and the two lines connecting the two contact points (P11, P12), respectively, the angle having a larger value among the angles When α is α, α < 360° at least immediately before the start of discharge, and the distance ℓ between the normal vectors at the two contact points P11 and P12 also has a value greater than 0.

Due to this, since the first compression chamber immediately before discharge has a smaller volume compared to the case in which the fixed lap and the orbital lap made of the involute curve have a smaller volume, the sizes of the first lap 323 and the second lap 332 are not increased. Both the compression ratio of the first compression chamber V1 and the compression ratio of the second compression chamber V2 may be improved without the need to do so.

Meanwhile, as described above, the second scroll 33 may be pivotably installed between the frame 31 and the fixed scroll 32 . An Oldham ring 35 for preventing rotation of the second scroll 33 is installed between the upper surface of the second scroll 33 and the lower surface of the frame 31 corresponding thereto. A sealing member 36 forming the back pressure chamber S1 to be performed may be installed.

In addition, an intermediate pressure space is formed outside the sealing member 36 by the oil supply hole 321a provided in the second scroll 32 . This intermediate pressure space communicates with the intermediate compression chamber V and may serve as a back pressure chamber as the intermediate pressure refrigerant is filled. Accordingly, the back pressure chamber formed inside the sealing member 36 as the center may be referred to as a first back pressure chamber S1 , and the intermediate pressure space formed outside the sealing member 36 may be referred to as a second back pressure chamber S2 . After all, the back pressure chamber S1 is a space formed by the lower surface of the frame 31 and the upper surface of the second scroll 33 with the sealing member 36 as the center. will be explained again with

On the other hand, the flow path separation unit 40 is installed in the intermediate space 10a, which is a gas oil space formed between the lower surface of the transmission unit 20 and the upper surface of the compression unit 30, the refrigerant discharged from the compression unit 30 is It serves to prevent interference with the oil moving from the upper space 10b of the electric part 20, which is the oil separation space, to the lower space 10c of the compression part 30, which is the storage space.

To this end, the flow path separation unit 40 according to the present embodiment separates the first space 10a into a space in which the refrigerant flows (hereinafter referred to as a refrigerant flow space) and a space through which oil flows (hereinafter, an oil flow space). Euro guide included. The flow guide may separate the first space 10a into a refrigerant flow space and an oil flow space with only the flow guide itself, but in some cases, a plurality of flow guides may be combined to serve as a flow guide.

The flow path separation unit according to the present embodiment includes a first flow path guide 410 provided on the frame 31 and extending upward, and a second flow path guide 420 provided on the stator 21 and extending downward. The first flow guide 410 and the second flow guide 420 overlap in the axial direction so that the intermediate space 10a can be separated into a refrigerant flow space and an oil flow space.

Here, the first flow guide 410 is manufactured in an annular shape and fixedly coupled to the upper surface of the frame 31 , and the second flow guide 420 is inserted into the stator 21 to extend from the insulator to insulate the winding coil. can

The first flow guide 410 includes a first round wall part 411 extending upward from the outside, a second round wall part 412 extending upward from the inside, and a first round wall part 411 and a second round wall part 412 ) consists of a circular surface portion 413 extending in the radial direction to connect between. The first round wall portion 411 is formed higher than the second round wall portion 412, and the refrigerant hole is formed in the round surface portion 413 so that the refrigerant hole communicating from the compression unit 30 to the intermediate space 10a communicates. can

And, the balance weight 26 is located inside the second round wall portion 412, that is, in the direction of the rotation axis, the balance weight 26 is coupled to the rotor 22 or the rotation shaft 50 and rotates. At this time, the balance weight 26 can stir the refrigerant while rotating, but it prevents the refrigerant from moving toward the balance weight 26 by the second round wall 412 so that the refrigerant is stirred by the balance weight 26 can be suppressed

The second flow guide 420 may include a first extension portion 421 extending downwardly from the outside of the insulator and a second extension portion 422 extending downwardly from the inside of the insulator. The first extension portion 421 is formed to overlap the first round wall portion 411 in the axial direction, and serves to separate the refrigerant flow space and the oil flow space. The second extension 422 may not be formed as needed, but even if it is formed, it does not overlap with the second round wall 412 in the axial direction or is formed at a sufficient distance in the radial direction so that the refrigerant can sufficiently flow even if it overlaps. It is preferable to be

On the other hand, the upper portion of the rotation shaft 50 is coupled to the center of the rotor 22, while the lower portion is coupled to the compression unit 30 may be supported in the radial direction. As a result, the rotation shaft 50 transmits the rotational force of the transmission unit 20 to the orbiting scroll 33 of the compression unit 30 . Then, the second scroll 33 eccentrically coupled to the rotation shaft 50 rotates with respect to the first scroll 32 .

A main bearing part (hereinafter, the first bearing part) 51 is formed in the lower half of the rotation shaft 50 so as to be inserted into the first bearing hole 312a of the frame 31 and supported in the radial direction, and the first bearing part ( A sub-bearing part (hereinafter, referred to as a second bearing part) 52 may be formed at a lower side of the first scroll 32 to be inserted into the second bearing hole 326a of the first scroll 32 and supported in the radial direction. And an eccentric part 53 may be formed between the first bearing part 51 and the second bearing part 52 to be inserted into and coupled to the rotation shaft coupling part 333 .

The first bearing part 51 and the second bearing part 52 are formed on a coaxial line to have the same axial center, and the eccentric part 53 is attached to the first bearing part 51 or the second bearing part 52 . It may be formed eccentric in the radial direction with respect to the. The second bearing part 52 may be formed to be eccentric with respect to the first bearing part 51 .

The eccentric part 53 must be formed to have an outer diameter smaller than the outer diameter of the first bearing part 51 and larger than the outer diameter of the second bearing part 52 so that the rotating shaft 50 is connected to each of the bearing holes 312a and 326a. It may be advantageous for coupling through the rotation shaft coupling portion 333 . However, when the eccentric portion 53 is not integrally formed with the rotation shaft 50 and is formed using a separate bearing, the outer diameter of the second bearing portion 52 is not formed smaller than the outer diameter of the eccentric portion 53 . It can be coupled by inserting the rotation shaft (50).

In addition, an oil supply passage 50a for supplying oil to each bearing portion and the eccentric portion may be formed in the rotation shaft 50 along the axial direction. The oil supply passage 50a is approximately at the lower end or intermediate height of the stator 21 from the lower end of the rotary shaft 50 as the compression unit 30 is located below the transmission unit 20, or the first bearing unit 31 It can be formed by a groove digging to a position higher than the top of the . Of course, in some cases, it may be formed to pass through the rotation shaft 50 in the axial direction.

In addition, an oil feeder 60 for pumping oil filled in the lower space 10c may be coupled to a lower end of the rotation shaft 50 , that is, a lower end of the second bearing unit 52 . The oil feeder 60 is composed of an oil supply pipe 61 inserted into and coupled to the oil supply passage 50a of the rotating shaft 50, and a blocking member 62 that accommodates the oil supply pipe 61 and blocks the intrusion of foreign substances. can The oil supply pipe 61 may pass through the discharge cover 34 and be positioned so as to be submerged in the oil of the lower space 10c.

On the other hand, as shown in Fig. 3, each of the bearing parts 51 and 52 and the eccentric part 53 of the rotating shaft 50 is connected to the oil supply passage 50a to supply oil to each sliding part. A channel F1 is formed.

The sliding part oil supply passage F1 includes a plurality of oil supply holes 511, 521 and 531 that penetrate from the oil supply passage 50a toward the outer circumferential surface of the rotary shaft 50, and each bearing portion 51 and 52. and a plurality of oil supply grooves 512 (512) ( 522) and 532.

For example, the first bearing part 51 has a first oil supply hole 511 and a first oil supply groove 512 , and the second bearing part 52 has a second oil supply hole 521 and a second oil supply groove ( 522, and the eccentric portion 53 is formed with a third oil supply hole 531 and a third oil supply groove 532, respectively. The first oil supply groove 512, the second oil supply groove 522, and the third oil supply groove 532 are each formed in a long groove shape in the axial direction or the oblique direction.

And, between the first bearing part 51 and the eccentric part 53, and between the eccentric part 53 and the second bearing part 52, the first connecting groove 541 and the second connecting groove each having an annular shape. 542 are respectively formed. The first connection groove 541 is connected to the lower end of the first oil supply groove 512 , and the second connection groove 542 is connected to the upper end of the second oil supply groove 522 . Accordingly, a portion of the oil lubricating the first bearing part 51 through the first oil supply groove 512 flows down to the first connection groove 541 and is collected, and this oil is transferred to the first back pressure chamber S1. It flows in to form a back pressure of the discharge pressure. In addition, the oil lubricating the second bearing portion 52 through the second oil supply groove 522 and the oil lubricating the eccentric portion 53 through the third oil supply groove 532 are connected to the second connection groove 542 . They may be gathered and introduced into the compression unit 30 through the front end surface of the rotation shaft coupling unit 333 and the first end plate 321 .

And a small amount of oil sucked in the upper end direction of the first bearing unit 51 flows out of the bearing surface from the upper end of the first bearing unit 312 of the frame 31 and flows along the first bearing unit 312 along the frame 31 ), after flowing down to the upper surface 31a of the frame 31 (or a groove communicating from the upper surface to the outer circumferential surface) of the frame 31 and the oil passage P _O1 continuously formed on the outer peripheral surface of the first scroll 32 ) (P O1 ) (P _O2 ) through the lower space (10c) is recovered.

In addition, oil discharged from the compression chamber (V) to the upper space (10b) of the casing (10) together with the refrigerant is separated from the refrigerant in the upper space (10b) of the casing (10), on the outer peripheral surface of the electric part (20) It is recovered to the lower space 10c through the formed first oil passage P _{O1 and the second oil passage P O2} formed on the outer peripheral surface of the compression unit 30 . At this time, the flow path separation unit 40 is provided between the electric part 20 and the compression part 30, and the oil separated from the refrigerant in the upper space 10b and moved to the heart space 10c is transferred to the compression part 20 ) and does not interfere with the refrigerant moving to the upper space 10b and do not _remix , and each oil flows through different passages [(P O1 )(P _O2 )][(P _G1 )(P _G2 )] into the lower space At (10c), the refrigerant can move to the upper space (10b).

On the other hand, the compression chamber oil supply passage F2 for supplying the oil sucked through the oil supply passage 50a to the compression chamber V is formed in the second scroll 33 . The compression chamber oil supply passage (F2) is connected to the sliding part oil supply passage (F1) described above.

The compression chamber oil supply passage F2 includes a first oil supply passage 371 communicating between the oil supply passage 50a and a second back pressure chamber S2 forming an intermediate pressure space, a second back pressure chamber S2 and It may be made of a second oil supply passage 372 communicating with the intermediate pressure chamber of the compression chamber (V).

Of course, the compression chamber oil supply passage may be formed to directly communicate with the intermediate pressure chamber from the oil supply passage 50a without passing through the second back pressure chamber S2. However, in this case, a refrigerant flow path connecting the second back pressure chamber S2 and the intermediate pressure chamber V must be separately provided, and for supplying oil to the Oldham ring 35 located in the second back pressure chamber S2. A separate oil path must be provided. As a result, the number of passages increases and processing becomes complicated. Therefore, in order to reduce the number of passages by unifying the refrigerant passage and the oil passage, as in the present embodiment, the oil supply passage 50a and the second back pressure chamber S2 are communicated, and the second back pressure chamber S2 is connected to the intermediate pressure chamber. It may be desirable to communicate with (V).

To this end, in the first oil supply passage 371 , a first turning passage portion 371a formed from the lower surface of the second end plate 331 to the middle in the thickness direction is formed, and in the first turning passage portion 371a A second turning passage part 371b is formed toward the outer circumferential surface of the second head plate part 331 , and a third turning passage part penetrating from the second turning passage part 371b toward the upper surface of the second end plate part 331 . (371c) is formed.

Further, the first turning passage portion 371a is formed at a position belonging to the first back pressure chamber S1 , and the third turning passage portion 371c is formed at a position belonging to the second back pressure chamber S2 . And a pressure reducing rod 375 in the second turning passage part 371b to lower the pressure of oil moving from the first back pressure chamber S1 to the second back pressure chamber S2 through the first oil supply passage 371 ) is inserted. Accordingly, the cross-sectional area of the second turning passage part 371b excluding the pressure reducing rod 375 is formed to be small in the first turning passage part 371a, the third turning passage part 371c, and the second turning passage part 371b.

Here, when the end of the third revolving passage portion 371c is formed to be located inside the Oldham ring 35, that is, between the Oldham ring 35 and the sealing member 36, the first oil supply passage 371 ), the oil moving through the Oldham ring 35 is clogged and cannot smoothly move to the second back pressure chamber S2. Accordingly, in this case, the fourth turning passage part 371d may be formed from the end of the third turning passage part 371c toward the outer peripheral surface of the second end plate part 331 . The fourth turning passage part 371d may be formed as a groove on the upper surface of the second end plate part 331 as shown in FIG. 4 , or may be formed as a hole inside the second end plate part 331 .

The second oil supply passage 372 has a first fixed passage portion 372a formed on the upper surface of the second side wall portion 322 in the thickness direction, and a second fixed passage in the radial direction from the first fixed passage portion 372a. A portion 372b is formed, and a third fixed passage portion 372c that communicates from the second fixed passage portion 372b to the intermediate pressure chamber V is formed.

In the drawings, an unexplained reference numeral 70 denotes an accumulator.

The lower compression type scroll compressor according to the present embodiment as described above operates as follows.

That is, when power is applied to the electric part 20, rotational force is generated in the rotor 21 and the rotating shaft 50 to rotate, and as the rotating shaft 50 rotates, the orbiting scroll eccentrically coupled to the rotating shaft 50 (33) is rotated by the Oldham ring (35).

Then, the refrigerant supplied from the outside of the casing 10 through the refrigerant suction pipe 15 flows into the compression chamber V, and the volume of the compression chamber V is reduced by the orbiting scroll 33's orbiting motion. As it decreases, it is compressed and discharged into the inner space of the discharge cover 34 through the discharge ports 325a and 325b.

Then, the refrigerant discharged into the inner space of the discharge cover 34 circulates in the inner space of the discharge cover 34, and after the noise is reduced, it moves to the space between the frame 31 and the stator 21, and this refrigerant is moved to the upper space of the electric part 20 through the gap between the stator 21 and the rotor 22 .

Then, after the oil is separated from the refrigerant in the upper space of the electric part 20, the refrigerant is discharged to the outside of the casing 10 through the refrigerant discharge pipe 16, while the oil is separated from the inner circumferential surface of the casing 10 and the stator ( 21) through the flow path and the flow path between the inner circumferential surface of the casing 10 and the outer circumferential surface of the compression part 30, a series of processes of recovery to the lower space 10c, which is the oil storage space of the casing 10, are repeated.

At this time, the oil in the lower space 10c is sucked through the oil supply passage 50a of the rotary shaft 50, and this oil is supplied through each oil supply hole 511, 521, 531 and oil supply groove 512, 522. ) 532 to lubricate the first bearing part 51 , the second bearing part 52 , and the eccentric part 53 , respectively.

Among them, the oil lubricating the first bearing part 51 through the first oil supply hole 511 and the first oil supply groove 512 is a first connection groove between the first bearing part 51 and the eccentric part 53 . 541, and this oil flows into the first back pressure chamber S1. This oil almost forms a discharge pressure, so that the pressure in the first back pressure chamber S1 also almost forms a discharge pressure. Accordingly, the central portion of the second scroll 33 can be supported in the axial direction by the discharge pressure.

Meanwhile, the oil in the first back pressure chamber S1 moves to the second back pressure chamber S2 through the first oil supply passage 371 due to the pressure difference with the second back pressure chamber S2 . At this time, a pressure reducing rod 375 is provided in the second swirl passage portion 371b constituting the first oil supply passage 371 , and the pressure of oil directed to the second back pressure chamber S2 is reduced to an intermediate pressure.

And, the oil moving to the second back pressure chamber (intermediate pressure space) S2 supports the edge of the second scroll 33 and at the same time, according to the pressure difference with the intermediate pressure chamber V, the second oil supply passage 372 is moved to the intermediate pressure chamber (V). However, when the pressure in the intermediate pressure chamber V becomes higher than the pressure in the second back pressure chamber S2 during the operation of the compressor, the refrigerant flows into the second back pressure chamber S2 through the second oil supply passage 372 in the intermediate pressure chamber V. ) will move towards In other words, the second oil supply passage 372 serves as a passage through which the refrigerant and the oil cross move according to the pressure difference between the pressure in the second back pressure chamber S2 and the intermediate pressure chamber V.

Meanwhile, as described above, a back pressure chamber is formed on the rear surface of the second scroll, that is, the upper surface of the second scroll, to prevent the second scroll from being pushed away from the first scroll by the pressure of the compression chamber.

That is, the back pressure chamber is provided with a sealing member on the lower surface of the frame and the upper surface of the second scroll, and the first back pressure chamber is formed between the second scroll and the frame, and the second back pressure chamber is formed between the second scroll and the frame and the first scroll, respectively. is formed

Accordingly, it is preferable that the sealing member has excellent sealing force between the frame and the second scroll, and has excellent wear resistance in consideration of friction caused by the revolving motion of the second scroll. In addition, since the sealing member seals in the axial direction while floating by pressure while being inserted into the sealing member insertion groove provided in the second scroll, it is preferable to be formed of a material and structure that can float quickly even at low pressure.

Meanwhile, as described above, as the first back pressure chamber, which is the central part of the second scroll, forms the discharge pressure, and the second back pressure chamber, which is the edge part, forms an intermediate pressure, the back pressure at the center of the second scroll, which is the orbiting scroll, increases from the edge part. A pressure higher than the back pressure of Meanwhile, the central portion of the second scroll is pressed more in the direction of the first scroll than the edge portion, and accordingly, the discharge end of the first lap positioned at the central portion of the first scroll is excessively pressed to the second end plate. At the same time, the central portion of the first wrap forms a discharge end to receive a discharge pressure, and the discharge end of the first wrap receives a strong gas force in the edge direction and centrifugal force generated during operation by this discharge pressure.

Accordingly, the discharge end of the first lap receives a pressing force from the central portion of the second scroll in the axial direction by the high back pressure of the first back pressure chamber, and at the same time receives a radial pressing force by the gas force of the discharge pressure, As a result, the discharge end of the first lap may be bent outward from the root of the lap toward the front end of the lap, that is, in the height direction of the lap.

Such a phenomenon may seriously occur when the second bearing hole through which the rotation shaft passes is formed in the center of the first scroll, which is a fixed scroll, as in the present embodiment. That is, when the second bearing hole is formed in the center of the first scroll, the discharge end of the first lap, which is a fixed lap, cannot be formed by extending to the center of the first scroll due to the second bearing hole. This is because the discharging end of is located far from the center of the scroll, so that the lap rigidity at the discharging end is lowered and the lap deformation increases.

And this phenomenon may occur more severely when the compression ratio is increased by changing the first wrap and the second wrap to an atypical shape as in the present embodiment. However, in this embodiment, the protrusion is formed at the discharge end of the first lap, so that the lap bearing force is improved to a certain extent. However, the lap bearing force does not increase as much as the compression ratio increases, so friction loss due to lap deformation at the discharging end of the first lap. However, there may be concerns about abrasion or rupture of the lap. FIG. 5 is a schematic view showing the amount of deformation around the discharge end of the first lap analyzed for each part to explain this, and FIG. 6 is a schematic diagram showing the shape of the wrap in the portion with the greatest amount of deformation in FIG. 5 from the front.

As shown in FIG. 5 , in the case of the first wrap 332 , the amount of deformation at the discharge end 323a is the largest by about 0.018 mm to 0.02 mm, and the amount of deformation gradually decreases from the discharge end 323a toward the suction end. can be seen doing In addition, it can be seen that the deformation amount of the first end plate portion 321 including the vicinity of the discharge end 323a of the first wrap 323 is approximately -0.003 mm to -0.005 mm. This can be seen that the first end plate portion 321 is slightly deformed by receiving a force in the opposite direction to the deformation of the first lap 323 .

Accordingly, as shown in FIG. 6 , the front end surface around the discharge end 323a receives a gas force and is bent from the right side of the drawing, that is, from the center to the edge, and the inner edge 323a1 of the discharge end 323a is the highest point. It faces the lower surface of the second end plate 331 while forming.

At the same time, the second scroll is moved by being pressed downward in the drawing by receiving the back pressure. However, as the discharge end 323a of the first wrap 323 is bent outwardly and deformed, the upper surface 321b of the first end plate 321 and the front end surface 332c of the second wrap 332 exert a back pressure. The discharge end 323a of the first wrap 323 and the lower surface 331b of the second end plate 331 first come into contact with each other before they come into contact with each other. That is, the distance t1 between the top surface of the first end plate part 321 and the front end surface 332c of the second wrap 332 is the discharge end 323a of the first wrap 323 and the second end plate part 331 . ) is larger than the interval t2 between the lower surfaces 331b. Accordingly, in a process in which the gap t2 between the front end surface 323c of the first wrap 323 and the lower surface 331b of the second end plate 331 is removed by the back pressure, the The friction loss or wear described above may occur between the upper surface 321b and the front end surface 332c of the second wrap 332 , and the vicinity of the discharge end of the first wrap may be broken.

In consideration of this, in this embodiment, by optimizing the lap height in the vicinity of the discharge end, the lap receives the axial force generated by the back pressure and the radial force generated by the gas force to a minimum, through which the lap and It is possible to suppress friction loss or abrasion between the end plates, or breakage of the lap. 7 to 10B are views showing this in detail.

As shown in these figures, the first lap 323 according to the present embodiment has a lap height gradually lowered from the end of the edge forming the suction end 323b to the end of the center forming the discharge end 323a. is formed Accordingly, it is possible to suppress excessive contact between the end surface of the lap at the center and the opposing end plate portion of the scroll. In general, in scroll compressors, the pressure and temperature of the compression chamber increase toward the center due to the characteristics of the scroll compressor, and the thermal expansion coefficient increases toward the center (discharge end) of the lap. However, as in the present embodiment, if the lap height is formed to be lower toward the center, it is possible to suppress excessive adhesion of the lap of the center to the end plate portion.

However, as the first wrap 323 according to the present embodiment is formed to increase the compression length of the first compression chamber V1 by abruptly bending the envelope together with the second wrap 332, the typical involute shape is Compared to the applied arc compression method, the compression ratio is greatly increased. As such, as the compression ratio of the first compression chamber V1 increases, the discharge end 323a of the first wrap 323 is radially (included in the axial direction, but schematically expressed in the radial direction) by the high-pressure gas force. ) is pushed to Accordingly, the tip of the lap of the discharge end 323a is bent outward, and the front end surface 323c of the discharge end 323a is in contact with the lower surface 331b of the second end plate 331 to the extent of the bending, so that wear may occur. have. Accordingly, in the present embodiment, the front end surface of the lap of the portion adjacent to the discharge end among the end surfaces of the lap of the first lap may be further inclined. 7 is a plan view showing the first scroll according to the present embodiment, and FIG. 8 is a schematic view showing the expanded first wrap having a two-stage inclined surface according to the present embodiment.

As shown in these figures, the first wrap 323 according to this embodiment is formed of a first inclined surface 323d having a first inclined processing amount from the suction end 323b to any one point A. and, from any one point A to the discharge end 323a, may be formed as a second inclined surface 323e having a second inclined machining amount greater than the first inclined machining amount. That is, as shown in FIG. 8 , the lap height H2 at any one point is lower than the lap height H1 at the suction end, and the lap height H3 at the discharge end is at an arbitrary point A. It is formed lower than the lap height (H2). The position of an arbitrary point A may be determined in consideration of the reliability of the compressor, which will be described later along with the range of the inclined surface.

Meanwhile, the second inclined surface may be formed on the entire front end surface of the lap from the discharge end to any one point, or may be formed at the inner edge of the discharge end in consideration of the outward bending of the vicinity of the discharge end. 9A and 9B are views showing the former, and FIGS. 10A and 10B are views showing the latter, respectively.

That is, as shown in FIG. 9A , the second inclined surface 323e according to the present embodiment is the front end surface 323c of the first lap 323 from the discharge end 323a to an arbitrary point A, as described above. ) can be formed with the same second inclined processing amount throughout. In this case, as shown in FIG. 9B , as the vicinity of the discharge end 323a is bent outward, the inner edge 323a1 faces the lower surface 331b of the second end plate 331 . However, even if the front end surface 332c of the second wrap 332 is in close contact with the upper surface 321b of the first end plate 321, the front end surface (inner edge) 323c of the first wrap 323 and the second end surface 323c The lower surface 331b of the part 331 is properly adhered to thereby suppressing friction loss or wear between the first wrap 323 and the second end plate 331 or damage to the wrap.

In addition, as in FIG. 10A , the second inclined surface 323e according to this embodiment is formed within the range from the discharge end 323a to an arbitrary point A, and more specifically, it is formed at the inner edge 323a1. can be Accordingly, when the front end surface 323c near the discharge end 323a is bent, the inner edge protrudes more than the outer edge side and comes into contact with the lower surface 331a of the second end plate 331 . However, when the second inclined surface 323e is formed by chamfering the inner edge, the height H3 of the discharge end of the first lap 323 in contact with the lower surface 331b of the second end plate 331 is lowered. 2 It is possible to suppress or minimize over-contact with the end plate 331 . In addition, since the second inclined surface 323e ideally forms a flat surface opposite to the second end plate 331 , it is possible to prevent the second end plate from coming into contact with a sharp part such as a corner. This means that when the second scroll 33 is made of an aluminum material that is relatively softer than that of the first scroll 32 , the second end plate 331 of the second scroll 33 becomes the first scroll 32 of the first scroll 32 . Abrasion by the wrap 323 can be effectively suppressed.

Accordingly, even when the first wrap 323 is bent outward near the discharge end, which is the center of the first scroll, the front end surface 323c of the first wrap 323 is on the lower surface 331b of the second end plate 331 . It is possible to suppress excessive adhesion and abrasion. This not only suppresses or minimizes wear generated when the first wrap 323 is bent, but also increases the pressure and temperature of the final compression chamber including the discharge end 323a significantly higher than the pressure and temperature of the upstream compression chamber. While the thermal expansion at the discharge end 323a is greatly increased, excessive contact with the second end plate 331 may be suppressed or minimized.

Here, the range of the second inclined surface 323e may be considered in terms of reliability. For example, if the second inclined surface 323e is formed only within a range that is too close to the discharge end 323a, the front end surface 323c of the first lap 323 is formed with the lower surface 331b of the second end plate 331 and The adhesion phenomenon cannot be sufficiently suppressed. That is, referring to FIG. 5 , it is preferable that the second inclined surface 323e be formed over the entire first section B1 in which the strain is at least 0.018 to 0.020 mm.

However, when the second inclined surface 323e does not include the entire area of the first section B1, the portion remaining in the first section B1, that is, the portion adjacent to the second section B2, is the first inclined surface 323d. ) while forming excessively close contact with the lower surface 331b of the second end plate 331, friction loss or wear may still occur, and the vicinity of the discharge end of the lap may be damaged. Conversely, if the second inclined surface 323e is formed with the same inclined processing amount up to the range too far from the discharge end 323a, that is, the second section B2 or more, the front end surface 323c of the first lap 323 and A gap may be generated between the second end plate portion 331 and the lower surface 331a, thereby causing refrigerant leakage.

Therefore, the range of the second inclined surface 323e formed by the second inclined processing amount is the first range B1 based on FIG. 5 , that is, when the discharge end 323a is 0°, the discharge end 323a is It is preferably formed to include at least a portion of the range from about 30 to 60°. More precisely, it may be preferable that the second inclined surface 323e is formed within a range of 0° to about 40 to 50°. In this case, the range in which the second inclined surface is formed may be formed to include the protrusion 328 of the first lap described above.

11 is a graph in which the efficiency and reliability of the inclined processing amount are compared and analyzed by specifying the range of the second inclined surface in the range of 0 to 45°. This is the analysis result by designing a lap height of 26mm and a maximum processing depth of 24㎛.

As shown, the front end surface 323c of the first wrap 323 is inclined with a single inclined surface from the discharge end (0°) 323a to the suction end (980°) 323b, but the discharge end 323a. In the case where the maximum processing depth was 32 μm, which is larger than that of this example, it was shown that the efficiency was decreased by about 4% compared to this example. This is because the processing depth in the vicinity of the discharge end 323a is excessively generated and the refrigerant leakage occurs accordingly.

In addition, the tip surface 323c of the first lap 323 is inclined with a single inclined surface from the discharge end 323a to the suction end 323b, but the maximum processing depth at the discharge end 323a is the same as in this embodiment 24 In the case of μm, it was shown that the efficiency was decreased by about 1% compared to this example. This is because frictional loss occurs in the vicinity of the discharge end 323a.

However, as in this embodiment, the first inclined surface 323d from the suction end 323b to the 45° point, and the second inclined surface 323e from the 45° point to the discharge end 323a, respectively, but the second inclined surface ( 323e) is larger than that of the first inclined surface 323d, and in the case of forming a two-stage inclined surface having a maximum processing depth of 24 μm at the discharge end 323a, it is higher than the previous two examples in terms of efficiency and reliability. showed remarkably good results.

For reference, as in this embodiment, the tip surface of the lap is formed with a first inclined surface and a second inclined surface based on 45°, but the maximum processing depth at the discharge end is 17 μm and the processing depth of 45° is set to this embodiment It can be seen that in the case of forming the same 10㎛ as , the efficiency is reduced by about 2%. This is because frictional loss occurs in the vicinity of the discharge end 323a.

Here, if the inclined processing amount of the first inclined surface and the inclined processing amount of the second inclined surface according to the present embodiment are respectively limited to numerical values, it will be as follows. That is, when the maximum height of the first lap is H1, the inclined processing amount on the first inclined surface is H2, and the inclined processing amount on the second inclined surface is H3,

H2 < [(0.001 to 0.002) × H1]mm,

It may be formed to satisfy H3 > [(0.01 to 0.03) × H1]mm.

On the other hand, another embodiment of the second inclined surface of the lap according to the present invention is as follows.

That is, in the above embodiment, the second inclined surface is formed with one inclination angle, but as shown in FIG. 12 , the second inclined surfaces 323e1 to 323e4 according to the present embodiment are formed with a plurality of inclination angles.

In this case, it is preferable that the inclination angle of the second inclined surfaces 323e1 to 323e4 is gradually increased toward the discharge end 323a in consideration of the amount of lap deformation.

In addition, as shown in 13a, the second inclined surface 332e according to the present embodiment is formed on the second lap 332 of the second scroll, which is an orbiting scroll, or as shown in FIG. 13B, the second inclined surface 323e according to the present embodiment. 332e may be respectively formed on the front end surfaces of the first wrap 323 and the second wrap 332 .

However, in the case of the second wrap 332 , as a thick rotation shaft coupling portion is formed at the discharge end, which is the center, there is no high risk that the discharge end of the second wrap 332 is deformed or damaged due to relatively high pressure. However, the discharge end of the second wrap 332 may also expand as the compression ratio increases, so that the temperature of the compression chamber rises, and the discharge end of the second wrap 332 forming the rotation shaft coupling portion may expand.

Then, the discharging end distal surface of the second lap 332 and the discharging discharging distal end surface of the second lap 332 are in excessive contact with the facing first end plate part 321, and the second wrap 332 or the first end plate Friction loss between the parts 321 may increase or wear may occur.

Even in this case, the second inclined surfaces 323e and 332e may be formed with one or a plurality of inclination angles. In addition, the basic configuration of the second inclined surface may be formed in the same manner as in the above-described embodiment. Therefore, a detailed description thereof will be omitted.

However, even when the second inclined surfaces 323e and 332e are formed on the first wrap 323 and the second wrap 332, respectively, the first wrap 323 and the second wrap 332 are the scrolls facing each other. Since it comes into contact with the end plate, it may be preferable that the amount of bevel processing of the first lap and the second lap is the same as that of the above-described embodiments.

10: casing 20: electric part
30: compression unit 31: frame
32: first scroll 323: first lap
323a: discharge end 323b: suction end
323c: front end surface 323d: first inclined surface
323e: second inclined surface 33: second scroll
332: second lap 40: flow path separation unit
50: rotation shaft 50a: oil supply passage
51: first bearing part 52: second bearing part
53: eccentric part 60: oil feeder
70: accumulator S1: first back pressure chamber
S2: second back pressure chamber V: compression chamber

Claims (14)

first lap; and
and a second wrap engaged with the first wrap and eccentrically coupled with respect to the center of rotation of the axis of rotation to form a compression chamber that moves toward the center together with the first wrap while rotating with respect to the first wrap, ,
At least one of the first wrap and the second wrap includes a plurality of inclined surfaces having at least two different inclination angles that are gradually lowered toward the center,
The plurality of inclined surfaces,
a first inclined surface that is an inclined surface from the edge-side end of the first or second wrap to a predetermined angle toward the center, and a second inclined surface that is an inclined surface from the first inclined surface to the center-side end,
The inclination angle of the second inclined surface is,
The scroll compressor is formed to be larger than the inclination angle of the first inclined surface. According to claim 1,
When the central side of the first wrap or the second wrap is referred to as a discharge end based on the rotation angle of the rotation shaft, and the discharge end is 0°,
The second inclined surface is formed to include at least a portion in a range of 0 to 60° with respect to a rotation angle of the rotation shaft. 3. The method of claim 2,
A rotation shaft coupling portion is formed in the center of the second wrap so that the rotation shaft overlaps and is coupled to the second wrap in a radial direction,
A concave portion for reducing the thickness of the wrap is formed on the outer surface of the rotation shaft coupling portion, and a protrusion portion is formed at the discharge end of the first wrap to engage the concave portion,
The portion where the second inclined surface is formed includes the protrusion. a first scroll including a first end plate in which a bearing hole through which a rotation shaft passes and a discharge port is formed around the bearing hole, and a first wrap protruding from one side of the first end plate; and
A second end plate having a rotating shaft coupling portion formed thereon so that a rotating shaft passing through the bearing hole of the first scroll is eccentrically coupled to a central portion thereof, is formed to protrude from one side of the second end plate, and is engaged with the first lap to form a compression chamber a second scroll comprising a second wrap to
Among the front end surface of the first lap facing the second end plate part and the tip surface of the second lap facing the first end plate part, the tip surface of at least one of the laps has a lap height gradually lowered toward the discharge end, which is the center. It is formed to have a plurality of inclined surfaces,
An inclination angle of the second inclined surface toward the discharge end among the plurality of inclined surfaces is formed to be greater than that of the first inclined surface farther from the discharge end,
The second inclined surface is
The scroll compressor is formed to have a plurality of inclination angles, and the inclination angle of the second inclined surface increases as it approaches the discharge end. 5. The method of claim 4,
The second inclined surface is
and a front end surface of the first wrap or a front end surface of the second wrap along a traveling direction of the first wrap or the second wrap. delete 5. The method of claim 4,
and the second inclined surface is formed at an edge on a side to which a gas force acts among both edges constituting the front end surface of the first lap or the second lap. delete delete 5. The method of claim 4,
A concave portion for reducing the thickness of the wrap is formed on the outer surface of the rotation shaft coupling portion, and a protrusion portion is formed at the discharge end of the first wrap to engage the concave portion,
and the second inclined surface is formed to include the protrusion. a casing in which oil is stored in the inner space;
a driving motor provided in the inner space of the casing;
a rotating shaft coupled to the driving motor;
a frame provided under the driving motor;
a first scroll provided under the frame, having a first wrap formed on one side thereof, a bearing hole through which the rotation shaft passes, and a discharge port formed around the bearing hole; and
A second wrap engaged with the first wrap is formed, and the rotation axis is eccentrically coupled to overlap the second wrap in a radial direction, and is compressed between the first scroll and the first scroll while pivoting with respect to the first scroll. a second scroll forming a thread;
It is provided between the frame and the second scroll to separate the gap between the frame and the second scroll into an inner gap on the center side and an outer gap on the edge side, and the oil sucked through the rotation shaft flows into the inner gap and back pressure a sealing member for forming a seal;
A first oil supply passage communicating between the inner gap and the outer gap is formed in the second scroll or the frame, and a second oil supply passage communicating between the outer gap and the compression chamber is formed in the first scroll,
At least one of the tip surface of the first wrap protruding downwardly toward the second scroll and the tip surface of the second wrap protruding upward toward the first scroll has a lap height gradually lowering toward the center. It is formed to have a plurality of inclined surfaces,
A second inclined surface of the discharge end adjacent to the discharge port among the plurality of inclined surfaces has a larger inclination angle than the first inclined surface farther from the discharge port,
The second inclined surface is
The scroll compressor is formed to have a plurality of inclination angles, and the inclination angle of the second inclined surface increases as it approaches the discharge end. 12. The method of claim 11,
When the discharge end of the first wrap or the second wrap is 0° based on the rotation angle of the rotation shaft,
A position where the first inclined surface and the second inclined surface meet is formed to include at least a portion in a range of 0 to 60° with respect to a rotation angle of the rotation shaft. 13. The method of claim 12,
When the maximum height of the first lap or the second lap is H1, the amount of inclined processing on the first inclined surface is H2, and the amount of inclined processing on the second inclined surface is H3,
H2 < [(0.001 to 0.002) × H1]mm,
H3 > [(0.01~0.03) ×H1]mm,
Scroll compressor, characterized in that it satisfies. 14. The method according to any one of claims 11 to 13,
A rotation shaft coupling portion is formed in the center of the second wrap so that the rotation shaft overlaps and is coupled to the second wrap in a radial direction,
A concave portion for reducing the thickness of the wrap is formed on the outer surface of the rotation shaft coupling portion, and a protrusion portion is formed at the discharge end of the first wrap to engage the concave portion,
and the second inclined surface is formed to include the protrusion.

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